US4421425A - Fixed fad thrust bearing - Google Patents
Fixed fad thrust bearing Download PDFInfo
- Publication number
- US4421425A US4421425A US06/379,198 US37919882A US4421425A US 4421425 A US4421425 A US 4421425A US 37919882 A US37919882 A US 37919882A US 4421425 A US4421425 A US 4421425A
- Authority
- US
- United States
- Prior art keywords
- pad
- ring
- oil
- thrust bearing
- cage
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
- F16C17/047—Sliding-contact bearings for exclusively rotary movement for axial load only with fixed wedges to generate hydrodynamic pressure
Definitions
- the present invention concerns a fixed pad thrust bearing for a turbomachine.
- the invention consists in a fixed pad thrust bearing for a turbomachine, comprising a thrust collar integral with a rotor of said turbomachine, a ring comprising two parts of equal size formed with fixed sector-shaped pads separated by radial grooves and disposed around said rotor, deformable means on which a rear surface of said ring bears, a fixed cage containing said ring and said deformable means, oil feed means discharging into said fixed cage, and an annular oil recovery chamber whence oil is evacuated by gravity through one or more passages in the lower part of said fixed cage, wherein each pad is delimited by first and second lateral edges, said first lateral edge being in advance of said second lateral edge in the direction of rotation of said collar, each pad has a front surface facing said collar and an outer edge facing a wall of said cage, each pad has in its front surface an opening adjacent said first lateral edge, which is delimited by first and second inner edges, which does not extend so far as the inner and outer edges of the pad and which is fed by a
- the advantages of the thrust bearing in accordance with the invention are due to the fact that there is no splashing of the oil in the thrust bearing because the oil is not injected between the fixed and moving parts, at which point the oil has no function, but instead adjacent the first lateral edge of each pad where it has an active role in creating an oil film between the pads and the thrust collar. Furthermore, by virtue of the grooves some of the hot oil, which has accomplished its task, may be evacuated.
- the thrust bearing comprises sealing means between said outer edges of said pads and said wall of said cage, preventing oil from said oil feed circuit leaking towards said rear surface of said ring or towards said grooves and said front surface of said pads, so limiting oil consumption.
- said sealing means comprise two thread-like seals surrounding said ring, one on each side of said orifices in said outer edges of said parts.
- FIG. 1 shows a thrust bearing in accordance with the invention.
- FIG. 2 is a front view of part of the ring of pads in accordance with the invention.
- FIG. 3 is a developed cross-section through the ring of pads in FIG. 2, along arcuate line III--III.
- FIG. 1 is a cross-section through the axis of the thrust bearing in accordance with the invention.
- the shaft 1 of the turbine comprises a thrust collar 2.
- the stator of the turbine comprises a thrust bearing cage 3 disposed around collar 2 and containing an elastic ring 4 lining the side of the thrust bearing cage opposite collar 2 and a ring 16 incorporating a number of sector-shaped pads 5 separated by radial grooves 26 formed in said ring 16, extending across the full width of ring 16.
- stator there is an annular oil feed chamber 6 into which an oil feed line 7 discharges.
- Passages 8 connect chamber 6 with the inside of thrust-bearing cage 3.
- a seal 9 is provided between shaft 1 and thrust bearing cage 3 so that oil cannot leak along shaft 1, thereby limiting shear stresses on the oil between shaft 1 and thrust bearing cage 3.
- annular oil recovery space 10 Oil being evacuated by gravity through one or more passages 11 in the lower part of cage 3.
- each pad 5 has a first, leading lateral edge 12 and a second trailing lateral edge 13, the latter trailing first lateral edge 12 in the direction of rotation of shaft 1 and collar 2.
- Grooves 26 are delimited by the second lateral edge 13 of one pad 5 and the first lateral edge 12 of the next following pad 5.
- Bore 22 feeds oil to a groove 23 machined in front surface 14 and extending along a radius from a point adjacent the outer edge 21 of the pad to a point adjacent the inner edge 24 of the pad, close to first lateral edge 12 of said pad.
- Groove 23 is delimited by a first, leading inner edge 33 and a second trailing inner edge 34, the latter trailing first inner edge 33 in the direction of rotation of shaft 1 and collar 2.
- Front surface 14 of each pad 5 faces collar 2 and incorporates a first plane surface 20 parallel to rear surface 15 of ring 16 extending from first lateral edge 12 to inner edge 33.
- a second plane surface 19 diverges from rear surface 15 of ring 16 in the direction from first inner edge 33 to second lateral edge 13.
- Rear surface 15 of ring 16 bears on elastic ring 4 via shallow bosses 27 formed on it.
- pivot pins 17 Fixed to ring 4 are pivot pins 17 each of which penetrates into a cylindrical bore 18 parallel to the axis of the turbomachine in rear surface 15 of ring 16 in line with each pad 5 and preventing rotation of ring 16 relative to elastic ring 4 which is itself keyed against rotation relative to thrust bearing cage 3 by a stop 35.
- the effect of the oil pressure is to move ring 16 away from collar 2, guided by pivot pins 17 which remain in their respective bores 18.
- Each passage 8 terminates in a space 28 formed in cage 3 facing orifice 32 of a respective bore 22.
- a first thread-like seal 29 runs around the ring so as to constitute a torus in the vicinity of rear surface 15 to form a seal between outer edge 21 of pads 5 and the wall of cage 3, to prevent oil leaking from spaces 28 towards rear surface 15.
- a second thread-like seal 30 runs around ring 6 in the vicinity of the bottoms 31 of grooves 26, forming a seal between outer edge 21 of pads 5 and the wall of cage 3 to prevent oil leaking from spaces 28 towards grooves 26.
- the cold oil is introduced directly beneath pads 5 without previously being subjected to significant shearing stresses between two surfaces in relative movement, especially in the vicinity of the rotor.
- the major part of the power consumed by the oil thus contributes to generating the hydrodynamic supporting force.
- collar 2 could comprise, on the side opposite that shown, a thrust bearing symmetrical so that shown relative to a plane perpendicular to the axis, in which case a common annular space 10 could serve to recover the oil from both bearings.
- the single groove 23 could be replaced with a series of circular openings disposed along a line in the vicinity of first lateral edge 12.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
- Supercharger (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR8109706A FR2505950A1 (fr) | 1981-05-15 | 1981-05-15 | Butee a patins fixes |
FR8109706 | 1981-05-15 |
Publications (1)
Publication Number | Publication Date |
---|---|
US4421425A true US4421425A (en) | 1983-12-20 |
Family
ID=9258498
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US06/379,198 Expired - Lifetime US4421425A (en) | 1981-05-15 | 1982-05-17 | Fixed fad thrust bearing |
Country Status (7)
Country | Link |
---|---|
US (1) | US4421425A (fr) |
EP (1) | EP0065696B1 (fr) |
JP (1) | JPS57200720A (fr) |
AT (1) | ATE17270T1 (fr) |
DE (1) | DE3268242D1 (fr) |
FR (1) | FR2505950A1 (fr) |
ZA (1) | ZA823399B (fr) |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3722127A1 (de) * | 1986-07-10 | 1988-01-14 | Dana Corp | Haltering, insbesondere fuer freilaufkupplung |
US5626470A (en) * | 1996-04-10 | 1997-05-06 | Ingersoll-Rand Company | Method for providing lubricant to thrust bearing |
US5795076A (en) * | 1995-10-13 | 1998-08-18 | Orion Corporation | Tilt pad hydrodynamic bearing for rotating machinery |
US5879085A (en) * | 1995-10-13 | 1999-03-09 | Orion Corporation | Tilt pad hydrodynamic bearing for rotating machinery |
US5951172A (en) * | 1995-10-13 | 1999-09-14 | Orion Corporation | Sleeve bearing lubrication |
US6024494A (en) * | 1998-02-12 | 2000-02-15 | Ingersoll-Dresser Pump Company | Polymer-backed thrust bearings |
US6460635B1 (en) | 1999-10-25 | 2002-10-08 | Kalsi Engineering, Inc. | Load responsive hydrodynamic bearing |
US20030039417A1 (en) * | 2001-06-05 | 2003-02-27 | Aguilar Scott Grover | Diverted flow thrust bearing |
US20060171616A1 (en) * | 2005-02-03 | 2006-08-03 | Kalsi Engineering, Inc. | Hydrodynamic thrust bearing assembly |
US9109703B2 (en) | 2010-02-11 | 2015-08-18 | Kalsi Engineering, Inc. | Hydrodynamic backup ring |
US9429238B2 (en) | 2009-11-30 | 2016-08-30 | Kalsi Engineering, Inc. | Dynamic backup ring assembly |
US9845879B2 (en) | 2009-11-30 | 2017-12-19 | Kalsi Engineering, Inc. | High pressure dynamic sealing arrangement |
US10330203B2 (en) | 2017-01-06 | 2019-06-25 | Kalsi Engineering Inc. | High pressure dynamic sealing device |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4311117A1 (de) * | 1993-04-05 | 1994-10-06 | Abb Management Ag | Axiales Gleit-Schublager, insbesondere für Turbolader |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1436265A (en) * | 1918-06-03 | 1922-11-21 | Kingsbury | Bearing |
US2731308A (en) * | 1952-08-30 | 1956-01-17 | Gen Electric | Self-aligning thrust bearing structure |
US3893737A (en) * | 1974-04-19 | 1975-07-08 | Marchem Resources Inc | Thrust bearing having lubrication system |
US3966279A (en) * | 1975-06-06 | 1976-06-29 | Westinghouse Electric Corporation | High-load capacity, non-tilting thrust bearing |
US3982796A (en) * | 1973-02-28 | 1976-09-28 | The Glacier Metal Company Limited | Thrust bearings |
US4277112A (en) * | 1979-10-01 | 1981-07-07 | Mechanical Technology Incorporated | Stepped, split, cantilevered compliant bearing support |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR484366A (fr) * | 1916-02-16 | 1917-10-02 | Charles Algernon Parsons | Perfectionnements au graissage de paliers de butée |
GB843021A (en) * | 1957-09-03 | 1960-08-04 | Napier & Son Ltd | Improvements relating to thrust bearings, face seals or the like |
GB1392245A (en) * | 1971-11-12 | 1975-04-30 | Schwermasch Liebknecht Veb K | Axial sliding bearings |
JPS5312009B2 (fr) * | 1974-02-01 | 1978-04-26 | ||
JPS5945850B2 (ja) * | 1979-07-13 | 1984-11-09 | 株式会社日立製作所 | スラスト軸受 |
-
1981
- 1981-05-15 FR FR8109706A patent/FR2505950A1/fr active Granted
-
1982
- 1982-05-11 DE DE8282104069T patent/DE3268242D1/de not_active Expired
- 1982-05-11 EP EP82104069A patent/EP0065696B1/fr not_active Expired
- 1982-05-11 AT AT82104069T patent/ATE17270T1/de not_active IP Right Cessation
- 1982-05-14 JP JP57082304A patent/JPS57200720A/ja active Granted
- 1982-05-17 US US06/379,198 patent/US4421425A/en not_active Expired - Lifetime
- 1982-05-17 ZA ZA823399A patent/ZA823399B/xx unknown
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1436265A (en) * | 1918-06-03 | 1922-11-21 | Kingsbury | Bearing |
US2731308A (en) * | 1952-08-30 | 1956-01-17 | Gen Electric | Self-aligning thrust bearing structure |
US3982796A (en) * | 1973-02-28 | 1976-09-28 | The Glacier Metal Company Limited | Thrust bearings |
US3893737A (en) * | 1974-04-19 | 1975-07-08 | Marchem Resources Inc | Thrust bearing having lubrication system |
US3966279A (en) * | 1975-06-06 | 1976-06-29 | Westinghouse Electric Corporation | High-load capacity, non-tilting thrust bearing |
US4277112A (en) * | 1979-10-01 | 1981-07-07 | Mechanical Technology Incorporated | Stepped, split, cantilevered compliant bearing support |
Cited By (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3722127A1 (de) * | 1986-07-10 | 1988-01-14 | Dana Corp | Haltering, insbesondere fuer freilaufkupplung |
US4757887A (en) * | 1986-07-10 | 1988-07-19 | Dana Corporation | Split thrust/retainer ring for an overrunning clutch |
US5795076A (en) * | 1995-10-13 | 1998-08-18 | Orion Corporation | Tilt pad hydrodynamic bearing for rotating machinery |
US5879085A (en) * | 1995-10-13 | 1999-03-09 | Orion Corporation | Tilt pad hydrodynamic bearing for rotating machinery |
US5951172A (en) * | 1995-10-13 | 1999-09-14 | Orion Corporation | Sleeve bearing lubrication |
US5626470A (en) * | 1996-04-10 | 1997-05-06 | Ingersoll-Rand Company | Method for providing lubricant to thrust bearing |
US6024494A (en) * | 1998-02-12 | 2000-02-15 | Ingersoll-Dresser Pump Company | Polymer-backed thrust bearings |
US6460635B1 (en) | 1999-10-25 | 2002-10-08 | Kalsi Engineering, Inc. | Load responsive hydrodynamic bearing |
US20030039417A1 (en) * | 2001-06-05 | 2003-02-27 | Aguilar Scott Grover | Diverted flow thrust bearing |
US6827494B2 (en) * | 2001-06-05 | 2004-12-07 | Honeywell International, Inc. | Diverted flow thrust bearing |
US20060171616A1 (en) * | 2005-02-03 | 2006-08-03 | Kalsi Engineering, Inc. | Hydrodynamic thrust bearing assembly |
US9429238B2 (en) | 2009-11-30 | 2016-08-30 | Kalsi Engineering, Inc. | Dynamic backup ring assembly |
US9845879B2 (en) | 2009-11-30 | 2017-12-19 | Kalsi Engineering, Inc. | High pressure dynamic sealing arrangement |
US9109703B2 (en) | 2010-02-11 | 2015-08-18 | Kalsi Engineering, Inc. | Hydrodynamic backup ring |
US10330203B2 (en) | 2017-01-06 | 2019-06-25 | Kalsi Engineering Inc. | High pressure dynamic sealing device |
Also Published As
Publication number | Publication date |
---|---|
FR2505950A1 (fr) | 1982-11-19 |
ZA823399B (en) | 1983-06-29 |
JPH028165B2 (fr) | 1990-02-22 |
ATE17270T1 (de) | 1986-01-15 |
EP0065696B1 (fr) | 1986-01-02 |
EP0065696A1 (fr) | 1982-12-01 |
DE3268242D1 (en) | 1986-02-13 |
JPS57200720A (en) | 1982-12-09 |
FR2505950B1 (fr) | 1985-04-26 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: SOCIETE ANONYME DITE: ALSTHOM-ATLANTIQUE 38, AVENU Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:ROUCHER, GERARD;HERMAND, MICHEL;REEL/FRAME:004175/0189 Effective date: 19820504 Owner name: SOCIETE ANONYME DITE: ALSTHOM-ATLANTIQUE, FRANCE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ROUCHER, GERARD;HERMAND, MICHEL;REEL/FRAME:004175/0189 Effective date: 19820504 |
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Free format text: PATENTED CASE |
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Free format text: PAYMENT OF MAINTENANCE FEE, 4TH YEAR, PL 96-517 (ORIGINAL EVENT CODE: M170); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY Year of fee payment: 4 |
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